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WO2016087849A1 - Soupape proportionnelle, et douche électrique et robinet incorporant la soupape proportionnelle - Google Patents

Soupape proportionnelle, et douche électrique et robinet incorporant la soupape proportionnelle Download PDF

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Publication number
WO2016087849A1
WO2016087849A1 PCT/GB2015/053680 GB2015053680W WO2016087849A1 WO 2016087849 A1 WO2016087849 A1 WO 2016087849A1 GB 2015053680 W GB2015053680 W GB 2015053680W WO 2016087849 A1 WO2016087849 A1 WO 2016087849A1
Authority
WO
WIPO (PCT)
Prior art keywords
armature
proportional valve
diaphragm plate
orifice
diaphragm
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/GB2015/053680
Other languages
English (en)
Inventor
Michael Quinn
Anton STEFANIC
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hydralectric Group Ltd
Eki d o o
Original Assignee
Hydralectric Group Ltd
Eki d o o
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from GBGB1421488.6A external-priority patent/GB201421488D0/en
Priority claimed from GBGB1517469.1A external-priority patent/GB201517469D0/en
Application filed by Hydralectric Group Ltd, Eki d o o filed Critical Hydralectric Group Ltd
Priority to EP15820569.0A priority Critical patent/EP3227593B1/fr
Priority to US15/532,545 priority patent/US11788644B2/en
Priority to ES15820569T priority patent/ES2838681T3/es
Publication of WO2016087849A1 publication Critical patent/WO2016087849A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/36—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor
    • F16K31/40—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor
    • F16K31/402—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor acting on a diaphragm
    • F16K31/404—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor acting on a diaphragm the discharge being effected through the diaphragm and being blockable by an electrically-actuated member making contact with the diaphragm
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D7/00—Control of flow
    • G05D7/005—Control of flow characterised by the use of auxiliary non-electric power combined with the use of electric means

Definitions

  • PROPORTIONAL VALVE ELECTRIC SHOWER INCORPORATING THE PROPORTIONAL VALVE AND TAP INCORPORATING SAME
  • This invention relates to a proportional valve which may be incorporated in an electric shower.
  • a proportional valve allows the flow rate to be varied throughout a range by varying the signal applied to a solenoid forming part of the proportional valve.
  • Proportional valves are known in which an input port is in fluid communication with a control chamber through small holes provided in a diaphragm.
  • the diaphragm carries a diaphragm plate that, when positioned in a main orifice between the input port and an output port, blocks the flow path between the input port and the output port except for a pilot orifice through the diaphragm plate.
  • the solenoid has an armature that, in the absence of a signal being applied to the field winding of the solenoid, is biased by a spring to pass through the control chamber and abut the diaphragm plate so as to move the diaphragm plate into the main orifice and to block the pilot orifice.
  • the fluid pressure in the control chamber assists in holding the diaphragm plate in the main orifice, so that no fluid flows from the inlet port to the outlet port when no signal is applied to the field winding of the solenoid.
  • proportional valves are desired that achieve average flows from 0.5 litres per minute to 12 litres per minute across 0.5 - 5 bar dynamic water pressure.
  • a problem with known proportional valves is that under mains water pressure, at low flow rates there is an initial, transient surge of water when the valve is first opened, before a steady state flow rate is achieved.
  • Previous attempts to address this problem have concentrated on the forces applied on the armature by the field winding of the solenoid and the spring. After much investigation, the present inventors have determined that the diaphragm plate and/or main orifice can be shaped in such a way as to inhibit transient fluid flow peaks.
  • the rate of increase in the pressure differential between the inlet port and control chamber sides of the diaphragm can be reduced, thereby slowing the lifting of the diaphragm plate out of the main orifice.
  • the part of the diaphragm plate that sits in the main orifice can be shaped so that the gap through to the main orifice increases approximately linearly with movement of the diaphragm plate.
  • Figure 1 shows a perspective view of a proportional valve according to the invention
  • Figure 2 shows a cross-section through the valve illustrated in Figure 1;
  • FIG 3 is an enlarged detail of the spring assembly of the valve illustrated in Figure 1;
  • Figure 4a shows a cross-section through a diaphragm plate forming part of the valve illustrated in Figure 1;
  • Figure 4b and 4c respectively show side and top views of the diaphragm plate
  • Figures 5a to 5e show the diaphragm plate at five different positions relative to the main orifice
  • Figure 6 illustrates an electronically-controlled shower system having hot and cold inlets, in which the flow rate through each inlet is controlled by the valve of Figure 1;
  • Figure 7 shows an electronically-controlled shower system having a cold inlet feeding into a heater, in which the flow rate through the cold inlet is controlled by the valve of Figure 1 ;
  • Figure 8 is an enlarged detail of part of the diaphragm plate of the valve of Figure 1 ;
  • Figure 9 is a plot of flow area against displacement of the diaphragm plate;
  • Figure 10 is a table of measurements of flow area against displacement of the diaphragm plate.
  • Figure 11 is a plot of bias sing force generated by the spring assembly of the valve illustrated in Figure 1.
  • a proportional valve 1 has an inlet port 3 and an outlet port 5.
  • the valve 1 includes a solenoid 7 having electrical contacts 9a and 9b.
  • the solenoid 7 is a 24V DC 8W solenoid.
  • the flow of liquid through the inlet port 3 of the proportional valve 1 to the outlet port 5 is controlled by an electrical signal applied to the solenoid 7 via the electrical contacts 9 a, 9b.
  • the proportional valve 1 has a housing 11 which defines the inlet port 3 and the outlet port 5, as well as defining a main orifice 20 between the inlet port 3 and the outlet port 5.
  • the housing 11 also defines a cylindrical guide tube 22, generally aligned with the main orifice 20, along which an armature 15 of the solenoid 7 can move along the cylindrical axis.
  • a spring chamber 23 is provided at the end of the guide tube 22 distal to the main orifice 20, and a control chamber 24 is formed at the end of the guide tube proximate the main orifice.
  • the housing 11 is formed of two members: the first member 11a defining the inlet port 3, the outlet port 5 and the main orifice 20; the second member 1 lb defining the spring chamber 23, guide tube 22 and control chamber 24.
  • Threading provided on an internal surface of the first housing member 11a and an external surface of the second housing member 1 lb enable the second housing member to be screw-fitted into the first housing member.
  • the housing 11 is made from moulded plastics, in particular glass-filled nylon.
  • a spring assembly 13 is provided in the spring chamber 23 and applies a biasing force to one end of the armature 15 urging it towards the main orifice 20.
  • a field winding 17 of the solenoid 7 is provided around the guide tube 22 housing the armature 15.
  • the armature 15 is made of a ferrous material so that a magnetic field generated by a current flowing through the field winding 17 exerts a force on the armature along the cylindrical axis.
  • the armature 15 is made of magnetic stainless steel, apart from a rubber boot 25 provided at the end of the armature 15 adjacent the main orifice 20.
  • an aperture for receiving the guide tube 22 is formed through the field winding 17 having a diameter of 8.8-8.9mm, which is a standard sizing for such a solenoid 7.
  • the thickness of the housing portion forming the guide tube 22 is 0.75mm, significantly less than for previous proportional valves, which allows for a larger diameter of 7mm for the armature 15 (compared to 6mm that is conventionally used). In this way, a stronger force can be applied to the armature 15 by current flowing in the field winding 17 than in comparison with the same current flowing in conventional proportional valves.
  • the use of magnetic stainless steel provides a comparatively low inertia system, which also assists in the controllability of the position of the armature 15 within the guide tube 22.
  • a small gap is provided between the armature 15 and the guide tube 22 so that the spring chamber 23 is in fluid communication with the control chamber 24.
  • a flexible diaphragm 19 is mounted in the housing 11 between the first housing member 11a and the second housing member 1 lb, so that the inlet port 3, outlet port 5 and main orifice 20 are on one side of the diaphragm 19 and the control chamber 24 and armature 15 are on the other side of the diaphragm 19.
  • Several small holes are provided in the diaphragm 19 to allow liquid to move from the inlet port 3 into the control chamber 24.
  • the diaphragm 19 carries a rigid diaphragm plate 21. As will be described hereafter, the positional relationship between the diaphragm plate 21 and the main orifice 20, which is controlled by the current flowing in the field winding 17, determines the flow rate through the valve 1.
  • a pilot orifice 31 is formed through the centre of the diaphragm plate 21, and is generally aligned with the cylindrical axis of the guide tube 22 which guides the movement of the armature 15.
  • the spring assembly 13 urges the armature 15 against the diaphragm plate 21, both inserting the diaphragm plate 21 into the main orifice 20 and blocking the pilot orifice 31 with the rubber boot 25. In this way, fluid flow between the inlet port 3 and the outlet port 5 is blocked. Further, fluid in the control chamber 24 applies pressure on the diaphragm 19 and diaphragm plate 21 that assists in holding the diaphragm plate 21 in the main orifice 20.
  • the present invention arises from the realisation that by careful design of the diaphragm plate 21 and the way that the diaphragm plate 21 sits in the main orifice 20, the sudden inflow of liquid through the main orifice as the diaphragm plate 21 lifts can be ameliorated.
  • the flow of liquid through the main orifice 20 typically increased exponentially with movement of the diaphragm plate 21 along the axis of movement of the armature.
  • the flow of liquid through the main orifice 20 can increase generally linearly with movement of the diaphragm plate 21 along the axis of movement of the armature 15.
  • the cross-section of the diaphragm plate 21 has three portions: an inverted frusto-conical portion 33, a neck portion 35 and a top portion 37.
  • the pilot orifice 31 has a narrow diameter portion 31a within the top portion 37 and a wider diameter portion 3 lb through the neck portion 35 and the top portion 37.
  • the diameter of the narrow portion 31a of the pilot orifice is 0.75mm, which is significantly less than that of pilot orifices for conventional proportional valves.
  • the rate of increase of the pressure differential when the pilot orifice 31 is first opened is less than for conventional proportional valves, which helps reduce the speed of movement of the diaphragm plate 21 and accordingly the rate of increase in the liquid flow through the main orifice.
  • an inlet filter (not shown) having a mesh size of 0.2mm is used.
  • the diameter of the wider portion 31b of the pilot orifice is 1.5mm. This offset in diameter between the narrow portion 31a and the wider portion 31b of the pilot orifice 31 assists in the moulding process for the diaphragm plate 21.
  • the diaphragm 19 is fitted around the neck portion 35 of the diaphragm plate 21, with the frustoconical section 33 on the main orifice side of the diaphragm and the top portion 37 on the control chamber side of the diaphragm 19.
  • the main part of the conical surface of the frusto- conical section 33 is sloped at an angle a of 39°, in contrast to previous diaphragm plates which typically slope away at a much larger angle apart from a number of radial guide fins.
  • the depth of the frusto-conical section is 3.25mm, significantly shorter than previous diaphragm plates.
  • a series of ribs 38 are evenly spaced about the conical surface of the frusto-conical section 33, in this case eight.
  • Each rib 38 has the same, substantially constant, depth. As well as reducing the possibility of the diaphragm plate 21 sticking in the main orifice, these ribs 38 further restrict the flow path for liquid to flow through the main orifice at low flow rates.
  • the diaphragm plate 21 presents a plain cylindrical surface, indicated by the letter A in Figure 8, extending parallel to the axis of the main orifice 20. From there, the surface of the diaphragm plate 21 extends away at an angle to produce its characteristic frusto-conical form.
  • the ribs 38 start at the junction of these two surfaces and initially extend parallel to the axis of the main orifice 20, flush with the plain cylindrical surface of the diaphragm plate 21, indicated in Figure 8 by the letter B. After a short distance, the ribs 38 turn and follow a path parallel to the frusto-conical surface of the diaphragm plate, but spaced from it, indicated in Figure 8 by the letter C.
  • this particular configuration of the ribs 38 will effect a variable rate of change of the annular space between the diaphragm plate 21 and the main orifice 20 as the diaphragm plate is drawn out of it.
  • This is deliberate and advantageous, because it can be designed to more closely mimic the ideal configuration which would bring about a linear rate of change of the annular gap.
  • the gap between the diaphragm plate 21 and the main orifice 20 varies in proportion to the square of the diameter, which implies that the ideal shape for the diaphragm plate would in fact be a parabolic curve, rather than frusto-conical.
  • Figures 5a to 5e show the position of the diaphragm plate 21 as it moves from the reset position, in which the main orifice 20 is closed, to a position in which the diaphragm plate is at the other end of its range of movement and the main orifice is fully open.
  • Table 1 below gives details of the main orifice 20 cross-section and extent of openness of the main orifice for the five positions of the diaphragm plate 21 shown in Figures 5a to 5e. It can be seen from the values given in Table 1 below that the cross-sectional area varies approximately linearly with the position of the diaphragm plate 21. This is significantly different from conventional proportional valves, in which the cross-sectional area increases exponentially with movement of the diaphragm plate.
  • the diaphragm plate 21 in this embodiment differs from those of conventional proportional valves in two main ways. Firstly, the pilot orifice 31 is narrower, which slows down the rate of increase in the pressure differential. Secondly, the portion of the diaphragm plate 21 that sits in the main orifice 20 is shaped so that the cross-sectional area available for fluid flow increases substantially linearly with movement of the diaphragm plate 21 out of the main orifice. These differences contribute to providing a significant improvement in the controllability of the flow rate through the valve in comparison with conventional valves, in particular by inhibiting transient liquid flow peaks through the output port 5 in response to initial unblocking of the main orifice 20.
  • FIG. 9 A plot of the rate of change of the annular gap between the diaphragm plate 21 and the main orifice 20, ie the flow area for passage of water, in the earlier stages of opening is seen in Figure 9.
  • the initial part of the plot represents the phase of withdrawal of the diaphragm plate 21 indicated by the letter A in Figure 8.
  • the remainder of the plot represents the phases of withdrawal indicated by the letters B and C in Figure 8, and it can be seen how this varies in a substantially linear manner. Measurements taken for an embodiment of the valve with this configuration are shown in Figure 10.
  • the proportional valve of this embodiment was designed for use in an electronically controlled shower system with signal voltage proportional to the target flow, thereby providing control of hot and or cold water flows.
  • the invention encompasses an electric shower including such proportional valves.
  • the electronically-controlled shower hot water and cold water are mixed, with the flow rates of the hot and cold water being controlled by a proportional valve as described above.
  • cold water flows from a cold water inlet to a first proportional valve 101a via a first temperature sensor 103 a.
  • the output of the first valve 101a flows to a mixing chamber 105 via a first flow meter 107a.
  • hot water flows from a hot water inlet to a second proportional valve 101b via a second temperature sensor 103b.
  • the output of the second valve 101b flows to the mixing chamber 105 via a second flow meter 107b.
  • the first and second temperature sensors 103 a, 103b and the first and second flow meters 107a, 107b are connected to a microcontroller 109.
  • a user control 111 via which the user of the shower indicates desired temperature and flow rate, is also connected to the microcontroller 109.
  • An algorithm within the microcontroller 109 calculates, based on the user-desired temperature and flow rate and the respective temperatures of the cold water and the hot water, required flow rates through the valves 101a, 101b and send control signals to the solenoids of the valves 101a, 101b to achieve those flow rates, as measured by the flow meters 107a, 107b.
  • the output of the mixing chamber 105 can be fed to the shower head (not shown) via a third temperature sensor 103c to verify that the temperature of the water supplied to the shower head matches the user-desired temperature.
  • the electronically-controlled shower heats cold water to a desired temperature, with the flow rate of the cold water being controlled by a proportional valve as described above.
  • cold water flows from a cold water inlet to a proportional valve 121 via a first temperature sensor 123 a.
  • the output of the valve 121 is directed to a heater 125 via a flow meter 127.
  • the first temperature sensor 123 a and the flow meter 127 are connected to a microcontroller 129.
  • a user control 131 via which the user of the shower indicates a desired temperature and flow rate, is also connected to the microcontroller 129.
  • An algorithm within the microcontroller 129 calculates, based on the user-desired temperature and the temperature of the cold water and the user-desired flow rate, a required flow rate through the valve 121 and a required heating power by the heater 125.
  • the microcontroller then sends a heater control signal to the heater to activate one or more heating elements to achieve the desired heating power, and a control signal to the valve 121 to achieve the desired flow rate, as measured by the flow meter 127.
  • the temperature of the water output by the heater is measured using a second temperature sensor 123b, as the microcontroller 129 can only provide coarse control of the heater 125. To provide fine temperature control, the microcontroller 129 varies the control signal to the valve 121 to achieve the desired temperature.
  • a feature of the proportional valve described above is that in addition to providing proportional flow control over 0.5-5 bar dynamic pressure, a simple on/off operation can take place as low as 0.2 bar static pressure. This means that it is not necessary to incoroporate separate on/off valves in the electronicaly-controlled showers in addition to the proportional valves.
  • a proportional valve as described above can be incorporated within an electronically-controlled shower to control the flow and temperature of water supplied to a shower head.
  • the proportional valve can be incorporated into a tap or faucet.
  • a tap or faucet for a mixer tap, an arrangement analogous to that of Figure 6 or that of Figure 7 could be used.
  • a hot tap or a cold tap may include a single proportional valve as described above.
  • the pilot orifice 31 has a portion with a diameter of 0.75mm, which was found to be generally optimal. Improvements can, however, be achieved with pilot orifices having a diameter of less than 0.8mm. Generally, the mesh size of the inlet filter should be less than 250 ⁇ .
  • cone angle of the frusto-conical section 33 of the diaphragm 19 in the embodiment described above is 39°, improvements can also be obtained with cone angles generally in the region of 30° to 45°.
  • the bias sing force for the armature is typically provided by a single constant-rate spring.
  • the armature 15 here is arranged to be biassed by means of a spring assembly 13 consisting of two springs 51, 52, rather than by a single spring.
  • the spring assembly 13 is arranged within the spring chamber 23, as with the single spring of a conventional valve.
  • the two springs 51, 52 are of different lengths and spring rates. They are also formed of different diameter coils, so that one is able to fit conveniently within the other (in this case, the longer spring 51 fitting inside the shorter one 52). Both springs 51, 52 have linear spring rates, with the longer one 51 having a lower spring rate than the shorter one 52, which is stiffer.
  • the longer spring 51 is installed in the spring chamber 23 so as to exert pre-compression on the armature 15. This is to ensure that the armature 15 will seat against the diaphragm plate 21 in the de-energised condition of the valve in any orientation, ie whether the valve 1 sits in a horizontal, vertical or otherwise inverted plane.
  • the seating of the armature 15 on the diaphragm plate 21 is necessary to ensure that the pilot orifice 31 will remain closed off when the valve is de-energised.
  • the shorter spring 52 exerts no biassing force on the armature 15.
  • Figure 11 shows in plot X how the biassing force applied by the spring assembly 13 varies with the position of the armature 15, as compared with plot Y for a conventional spring arrangement.
  • the biassing force acting on the armature 15 is generally at a lower spring rate than in a conventional valve.
  • the initial movement of the armature 15 will be resisted mostly by the softer spring 51.
  • the configuration and characteristics of the two springs 51, 52 in the spring assembly 13 can be tailored to provide a wide variety of different biassing actions. It will also be appreciated that the spring assembly 13 could take other forms, for example by incorporating more than two springs, or possibly by consisting of a single spring with a non-linear spring rate.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

L'invention concerne une soupape proportionnelle comprenant un orifice d'entrée (3), un orifice de sortie (5) séparés par une membrane (19). Une plaque de membrane (21) dotée d'un orifice pilote (31) formé à travers ladite membrane est montée sur cette dernière (19). La soupape comprend un solénoïde (7) composé d'un induit (15) et d'un enroulement de champ (17), l'induit étant mobile dans un sens d'ouverture en réponse à un champ magnétique généré par l'enroulement de champ. Un ensemble ressort (13) est agencé pour appliquer une force de sollicitation sur l'induit (15) dans son sens de fermeture. En position fermée, la plaque de membrane (21) repose dans un orifice principal (20) entre les orifices d'entrée et de sortie pour bloquer l'écoulement de fluide entre eux, l'induit (15) bloquant l'orifice pilote (31). Le mouvement d'ouverture de l'induit (15) fait s'ouvrir l'orifice pilote (31) pour permettre l'écoulement du fluide à travers celui-ci, ce qui permet ensuite le déplacement de la plaque de membrane (21) hors de l'orifice principal (20) pour créer un espace permettant l'écoulement du fluide de l'orifice d'entrée (3) vers l'orifice de sortie (5). La plaque de membrane (21) et l'orifice principal (20) sont conçus de telle sorte que pendant le mouvement d'ouverture initial de la plaque de membrane, le taux d'augmentation de l'espace entre ceux-ci varie approximativement de manière linéaire.
PCT/GB2015/053680 2014-12-03 2015-12-02 Soupape proportionnelle, et douche électrique et robinet incorporant la soupape proportionnelle Ceased WO2016087849A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP15820569.0A EP3227593B1 (fr) 2014-12-03 2015-12-02 Soupape proportionnelle, et douche électrique et robinet incorporant la soupape proportionnelle
US15/532,545 US11788644B2 (en) 2014-12-03 2015-12-02 Proportional valve, electric shower incorporating the proportional valve and tap incorporating same
ES15820569T ES2838681T3 (es) 2014-12-03 2015-12-02 Válvula proporcional, ducha eléctrica que incorpora la válvula proporcional y grifo que incorpora la misma

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
GB1421488.6 2014-12-03
GBGB1421488.6A GB201421488D0 (en) 2014-12-03 2014-12-03 Proportional valve and electric shower incorporating the proportional valve
GB201422031 2014-12-11
GB1422031.3 2014-12-11
GBGB1517469.1A GB201517469D0 (en) 2014-12-03 2015-10-02 Proportional valve and electric shower incorporating the proportional valve
GB1517469.1 2015-10-02

Publications (1)

Publication Number Publication Date
WO2016087849A1 true WO2016087849A1 (fr) 2016-06-09

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PCT/GB2015/053680 Ceased WO2016087849A1 (fr) 2014-12-03 2015-12-02 Soupape proportionnelle, et douche électrique et robinet incorporant la soupape proportionnelle

Country Status (4)

Country Link
US (1) US11788644B2 (fr)
EP (1) EP3227593B1 (fr)
ES (1) ES2838681T3 (fr)
WO (1) WO2016087849A1 (fr)

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EP0489331A1 (fr) * 1990-12-05 1992-06-10 A. und K. Müller GmbH & Co. KG Soupape actionnée par son propre fluide et commandée par un électro-aimant
DE19545532A1 (de) * 1994-12-12 1996-06-13 Elbi Int Spa Halte- und Führungseinheit für ein Sperrorgan eines Solenoidventils und Verfahren zu ihrer Herstellung
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EP1431640A1 (fr) * 2002-12-19 2004-06-23 A. und K. Müller GmbH & Co. KG Dispositif de soupape avec une servovanne controlée par un moteur électrique
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ES2838681T3 (es) 2021-07-02
EP3227593B1 (fr) 2020-09-30
US11788644B2 (en) 2023-10-17
US20170363224A1 (en) 2017-12-21
EP3227593A1 (fr) 2017-10-11

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